U.S. patent application number 16/630828 was filed with the patent office on 2020-05-07 for disc brake, disc brake system, and parking brake system.
This patent application is currently assigned to ZF Active Safety GmbH. The applicant listed for this patent is ZF Active Safety GmbH. Invention is credited to Frank Wilhelm Madzgalla, Christian Schroeter, Guido Zenzen.
Application Number | 20200141456 16/630828 |
Document ID | / |
Family ID | 62975813 |
Filed Date | 2020-05-07 |
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United States Patent
Application |
20200141456 |
Kind Code |
A1 |
Zenzen; Guido ; et
al. |
May 7, 2020 |
DISC BRAKE, DISC BRAKE SYSTEM, AND PARKING BRAKE SYSTEM
Abstract
The invention relates to a disc brake, comprising a brake
carrier, a brake caliper, brake shoes, and an actuating piston. The
brake carrier has at least one mounting point for mounting on a
vehicle. The actuating piston is displaceably accommodated on the
brake caliper and is actuatable for carrying out a service brake
function of the disc brake. At least one further actuating piston
is provided, which in the direction of its longitudinal axis is
displaceably accommodated on the brake caliper. For carrying out
the service brake function, the at least two actuating pistons are
actuatable, and for carrying out a parking brake function, one of
the actuating pistons is actuatable. The invention further relates
to a disc brake system and a parking brake system.
Inventors: |
Zenzen; Guido; (Macken,
DE) ; Madzgalla; Frank Wilhelm; (Koblenz, DE)
; Schroeter; Christian; (Sinzing, DE) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
ZF Active Safety GmbH |
Koblenz |
|
DE |
|
|
Assignee: |
ZF Active Safety GmbH
Koblenz
DE
|
Family ID: |
62975813 |
Appl. No.: |
16/630828 |
Filed: |
July 5, 2018 |
PCT Filed: |
July 5, 2018 |
PCT NO: |
PCT/DE2018/100617 |
371 Date: |
January 13, 2020 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F16D 65/0093 20130101;
B60T 13/12 20130101; F16D 2055/0016 20130101; F16D 55/16 20130101;
B60T 1/065 20130101; F16D 55/18 20130101; F16D 65/183 20130101;
B60T 13/741 20130101; F16D 55/228 20130101; F16D 55/227 20130101;
F16H 2025/2081 20130101; F16D 65/0087 20130101; F16D 2055/0008
20130101; F16D 2121/24 20130101; F16D 2125/40 20130101; F16D
65/0068 20130101; B60T 13/746 20130101; F16H 25/20 20130101; F16D
65/0056 20130101; B60T 13/58 20130101; B60T 11/10 20130101; F16D
2121/04 20130101 |
International
Class: |
F16D 55/227 20060101
F16D055/227; F16D 65/00 20060101 F16D065/00; F16D 65/18 20060101
F16D065/18; B60T 13/74 20060101 B60T013/74; F16H 25/20 20060101
F16H025/20; B60T 1/06 20060101 B60T001/06; B60T 13/58 20060101
B60T013/58 |
Foreign Application Data
Date |
Code |
Application Number |
Jul 19, 2017 |
DE |
10 2017 116 323.9 |
Claims
1. A disc brake, comprising: a brake carrier, a brake caliper, a
plurality of brake shoes, and an actuating piston, wherein the
brake carrier has at least one mounting point for mounting on a
vehicle, and the brake caliper is guided on the brake carrier and
has a receiving space for a brake disc, and the receiving space has
two brake sides with regard to the brake disc, wherein the brake
shoes are associated with the brake sides and are supported on the
brake carrier against braking forces; and wherein the actuating
piston in a direction of its longitudinal axis is displaceably
accommodated on the brake caliper and is actuatable for carrying
out a service brake function of the disc brake, and wherein the
actuating piston is actuatable by means of an electric motor for
carrying out a parking brake function of the disc brake, such that
at least one further actuating piston is provided, which in a
direction of its longitudinal axis is displaceably accommodated on
the brake caliper, wherein for carrying out the service brake
function the at least two actuating pistons are actuatable, and for
carrying out the parking brake function, one of the actuating
pistons is actuatable.
2. The disc brake according to claim 1, wherein, on at least one of
the brake sides, at least two of the brake shoes are spaced apart
from one another, and in each case one of the actuating pistons is
associated with the at least two brake shoes.
3. The disc brake according to claim 1 wherein at least two of the
brake shoes are spaced apart from one another on both brake sides,
and one of the actuating pistons is in each case associated with
the brake shoes of one of the brake sides, and the brake caliper is
displaceably guided on the brake carrier by at least one,
preferably two, guide elements, wherein the guide elements are
situated between the brake shoes of the respective brake side.
4. The disc brake according to claim 3 wherein the actuating
pistons are situated on the brake caliper symmetrically with
respect to an axial center plane of the brake carrier, and the
guide elements are situated in the axial center plane and spaced
apart from one another in the radial direction with respect to a
center axis of the disc brake.
5. The disc brake according to claim 3 wherein the electric motor
is situated between the actuating pistons, and a longitudinal axis
of the electric motor and/or an output shaft of the electric motor
and the longitudinal axis of the actuating piston that is
actuatable by the electric motor are axially offset relative to one
another, in particular situated axially parallel to one
another.
6. The disc brake according to claim 3 wherein the electric motor
engages with an open space of the brake caliper.
7. The disc brake according to claim 3 wherein the longitudinal
axis of the electric motor and/or the output shaft of the electric
motor coincide with the center axis of the disc brake.
8. The disc brake according to claim 3 wherein the electric motor
is operatively connectable to the one actuating piston via a screw
gear in order to carry out the parking brake function.
9. The disc brake according to claim 8 wherein the one actuating
piston is designed as a hollow piston that is open on one side, and
that with a closed side faces the associated brake side, and the
screw gear is at least partially situated in an interior space of
the one actuating piston.
10. The disc brake according to claim 9 wherein the service brake
function of the disc brake is carried out by hydraulic actuation of
the actuating pistons, and the interior space of the one actuating
piston forms a hydraulic chamber.
11. The disc brake according to claim 3 wherein the electric motor
and the screw gear are in drive connection with one another via a
reduction gear.
12. The disc brake according to claim 8 wherein the screw gear has
a spindle/nut arrangement, and has a threaded spindle and a nut
element that meshes therewith.
13. The disc brake according to claim 12 wherein the threaded
spindle is displaceably fixed with respect to the brake caliper in
a direction of a longitudinal axis of the spindle/nut arrangement
and is rotatable about the longitudinal axis of the spindle/nut
arrangement, and the nut element is rotationally fixed with respect
to the one actuating piston and is displaceable in the direction of
the longitudinal axis of the one actuating piston, so that the nut
element is translationally moved either into contact with the one
actuating piston or away from the one actuating piston due to a
rotational motion of the threaded spindle, depending on its
rotational direction.
14. The disc brake according to claim 12 wherein the nut element is
displaceably fixed with respect to the brake caliper in the
direction of the longitudinal axis of the spindle/nut arrangement
and is rotatable about the longitudinal axis of the spindle/nut
arrangement, and the threaded spindle is rotatably fixed with
respect to the one actuating piston and is displaceable in the
direction of the longitudinal axis of the one actuating piston, so
that the threaded spindle is translationally moved either into
contact with the one actuating piston or away from the one
actuating piston due to a rotational motion of the nut element,
depending on its rotational direction.
15. The disc brake according to claim 12 wherein the thread of the
spindle/nut arrangement is self-locking.
16. The disc brake according to claim 15 wherein the brake caliper
is designed as a floating frame.
17. (canceled)
18. (canceled)
19. (canceled)
Description
CROSS-REFERENCE TO RELATED APPLICATION
[0001] This application is a national stage of International
Application No. PCT/DE2018/100617, filed Jul. 5, 2018, the
disclosure of which is incorporated herein by reference in its
entirety, and which claimed priority to German Patent Application
No. 102017116323.9, filed Jul. 14, 2017, the disclosure of which is
incorporated herein by reference in its entirety.
TECHNICAL FIELD
[0002] The invention relates to a disc brake having a brake
carrier, a brake caliper, brake shoes, and an actuating piston. The
invention further relates to a disc brake system and a parking
brake system.
BACKGROUND
[0003] A disc brake of the type discussed here is known from WO
99/05011 A1, in which it is used as a vehicle brake. A brake
carrier, a brake caliper, brake shoes, and an actuating piston are
provided in the disc brake. The brake carrier has at least one
mounting point for mounting on a vehicle. The brake caliper is
guided on the brake carrier and forms a receiving space for a brake
disc, the receiving space having two brake sides with regard to the
brake disc. The brake shoes are associated with the brake sides and
are supported on the brake carrier against braking forces. The
actuating piston in the direction of its longitudinal axis is
displaceably accommodated on the brake caliper, and can be actuated
hydraulically or by means of an electric motor. The disc brake
carries out a service brake function as a result of the hydraulic
actuation of the actuating piston. The actuating piston is
actuatable by the electric motor for carrying out a parking brake
function.
SUMMARY
[0004] It is an object of the invention to provide a disc brake
having features stated at the outset, which on the one hand
includes the above-described concept of the combination of a
service brake function and a parking brake function, and on the
other hand is refined along the lines of a high-performance brake.
A further aim is to provide a disc brake system and a parking brake
system that are suitable for the use of such a high-performance
brake.
[0005] This object is achieved with a disc brake having the
features of claim 1. To achieve the object, in addition a disc
brake system having the features of claim 15 and a parking brake
system having the features of claim 16 are proposed. Advantageous
embodiments and/or configurations and/or aspects of the invention
result from the subclaims, the following description, and the
figures.
[0006] A basic disc brake has a brake carrier, a brake caliper,
brake shoes, and an actuating piston. The brake carrier has at
least one mounting point for mounting on a vehicle. For example,
the mounting point has a through opening, in particular a through
borehole, or a blind hole, in particular a blind borehole, or is
formed therefrom. The brake caliper is guided on the brake carrier,
and has or forms a receiving space for a brake disc, or at least
for a circular section or a circular segment of a brake disc, the
receiving space has two brake sides with regard to the brake disc.
The brake shoes are associated with the brake sides and supported
on the brake carrier against braking forces. The actuating piston
in the direction of its longitudinal axis is displaceably
accommodated on the brake caliper, and is actuatable for carrying
out a service brake function of the disc brake. In addition, the
actuating piston is actuatable by means of an electric motor for
carrying out a parking brake function of the disc brake.
[0007] According to one embodiment of the disc brake, at least one
further actuating piston is provided, which in the direction of its
longitudinal axis is displaceably accommodated on the brake
caliper, wherein for carrying out the service brake function, the
at least two actuating pistons are actuatable, and for carrying out
the parking brake function, one of the actuating pistons is
actuatable, which for this purpose is actuated or actuatable by
means of the electric motor. In this way, a measure along the lines
of a high-performance brake is taken, since the at least two
actuating pistons may be used for carrying out the service brake
function, and thus, the force of the at least two actuating pistons
is available for service braking. At the same time, it has been
found that for carrying out the parking brake function, it is
sufficient to make use of one of the actuating pistons, in
particular only one of the actuating pistons. This is because the
aim of the parking brake function is to hold a vehicle equipped
with the disc brake at a standstill, and in this regard, the
vehicle is already stopped or at least essentially stopped
beforehand.
[0008] The term "service brake function" is understood in
particular to mean a function of the disc brake via which the
vehicle is equipped with the disc brake is braked and/or may be
braked to a standstill during operation, for example during travel.
Such service braking may be initiated by the vehicle driver, for
example by actuating the brake pedal, or an automatic driving
and/or braking control, such as adaptive cruise control.
[0009] The term "parking brake function" is understood in
particular to mean a function of the disc brake via which a vehicle
equipped with the disc brake is held at a standstill when the
parking brake function takes place. The aim is to prevent the
vehicle from inadvertently rolling away, also when the vehicle is
on an inclined roadway. The parking brake function is also referred
to below as hand brake function. In addition, the term "hand brake
function" is used below as a synonym for the term "parking brake
function." The parking brake function may, in principle, also be
used for emergency braking of the vehicle. The parking brake
function, therefore also implies an emergency brake function.
[0010] In one possible embodiment of the disc brake, on at least
one of the brake sides, at least two of the brake shoes are spaced
apart from one another, and in each case, one of the actuating
pistons is associated with the at least two brake shoes. In
particular, the spaced-apart brake shoes are independently, for
example separately, removable and/or, for example, separately
actuatable. Due to the separate arrangement between the two brake
shoes, a space is to be provided via which cooling of the brake
disc during a braking operation is facilitated. During the braking
operation, a friction area of the brake disc, which is initially in
frictional contact with one of the two brake shoes, does not come
into frictional contact with the other of the two brake shoes until
the space has been passed by. Thus, over a period of time, even if
it is very short, the stated friction area of the brake disc
experiences no further friction stress, and thus no further
heating. Any structural changes in the brake disc are counteracted
by this measure. In addition, possible vibration excitation of the
brake shoes is thus counteracted. In this regard, the aim is to
take this measure along the lines of a high-performance brake.
[0011] In addition, at least two of the brake shoes may be spaced
apart from one another, on the other brake side. In particular, it
is provided that on each of the two brake sides, at least two of
the brake shoes are spaced apart from one another, and one of the
actuating pistons is associated with the brake shoes of one of the
brake sides. For example, it is provided that the brake caliper is
displaceably guided on the brake carrier by at least one,
preferably two, guide elements. In this case, the guide elements
may be situated between the brake shoes of the respective brake
side. A compact design of the disc brake is thus facilitated. For
example, the guide elements are situated in the space between the
actuating pistons of the respective brake side. The guide elements,
as guide bolts or the like, may be designed as a component that
carries out a guiding function.
[0012] It is suitable for the actuating pistons to be situated on
the brake caliper symmetrically with respect to an axial center
plane of the brake carrier. It is also suitable for the guide
elements to be situated in the axial center plane. Furthermore, it
is suitable for the guide elements to be spaced apart from one
another in the radial direction with respect to the center axis of
the disc brake. A symmetrical force distribution during the service
braking is facilitated due to these geometric relationships. In
this regard, the aim is also to take these measures along the lines
of a high-performance brake. The center axis is understood in
particular to mean the longitudinal axis that extends in the center
with respect to the brake carrier and/or the brake caliper.
[0013] High braking forces may be transmitted from the brake
caliper to the brake carrier by the at least two guide elements. As
a result of the two guide elements being spaced apart from one
another in the radial direction with respect to the center axis of
the disc brake, possible tilting due to lateral tipping of the
brake caliper with respect to the brake carrier is counteracted
during a parking brake function. This takes place against the
background that during the parking brake function, only one of the
actuating pistons is actuated, and an asymmetrical force
distribution may thus take place.
[0014] In another embodiment of the disc brake, it is provided that
the brake caliper is designed as a floating frame. A measure is
thus also taken along the lines of a high-performance brake, since
the frame design of the brake caliper facilitates absorption of
high braking forces. To implement the parking brake function at the
disc brake with a preferably compact arrangement of the component
necessary for this purpose, it is suitable for the electric motor
to be situated between the actuating pistons. It is also suitable
for the longitudinal axis of the electric motor and/or an output
shaft of the electric motor and the longitudinal axis of the
actuating piston that is actuatable by the electric motor to be
axially offset relative to one another, in particular situated
axially parallel to one another. For example, it is provided that
the electric motor engages with an open space of the brake caliper,
in particular between the actuating pistons. For example, it is
also provided that the longitudinal axis of the electric motor
and/or the output shaft of the electric motor coincide(s) or
essentially coincide(s) with the center axis of the disc brake. The
center axis is understood in particular to mean the longitudinal
axis that extends in the center with respect to the brake carrier
and/or the brake caliper.
[0015] To allow the one actuating piston to be actuated by means of
the electric motor and thus to allow the parking brake function to
be carried out, according to one embodiment it is provided that the
electric motor is operatively connectable to the one actuating
piston via a screw gear and/or a lifting gear, in particular a
spindle lifting gear. A rotational motion carried out by the output
shaft of the electric motor is thus converted into a translational
motion for actuating the one actuating piston. For example, the one
actuating piston is designed as a hollow piston that is open on one
side, and that with a closed side faces the associated brake side;
the screw gear or the lifting gear is at least partially situated
in the interior space of the one actuating piston. As a result, the
screw gear or lifting gear is compactly accommodated in the disc
brake.
[0016] The service brake function of the disc brake may thus be
implemented by hydraulically actuating the actuating pistons to
carry out the service brake function. The service brake function of
the disc brake is then carried out by hydraulic actuation of the
actuating pistons. For this purpose, it may be provided that, for
example, the interior space of the one actuating piston, which is
utilizable for parking braking, forms a hydraulic chamber. A high
level of component integrity is thus achieved, since the interior
space of the one actuating piston assumes a dual function, namely,
is used as a receiving space for the screw gear or the lifting
gear, and serves as a hydraulic chamber. In principle, the other
actuating piston may also be designed as a hollow piston whose
interior space serves as a hydraulic chamber.
[0017] In one possible embodiment of the disc brake, the electric
motor and the screw gear or the lifting gear may be in drive
connection with one another via a reduction gear. The reduction
gear may be designed as a planetary gear, strain wave gear,
eccentric disc gear, or swash plate gear. These types of gears are
compact, and have good efficiency with a low weight.
[0018] The reduction gear may also have a one-stage or also
multi-stage, in particular two-stage, design. To save installation
space, a two-stage gear may be provided whose one-stage is formed
by one of the above-mentioned gear types having a reduction in the
range of 50:1, to which a second stage having a reduction in the
range of 4:1 is connected upstream or downstream, so that an
overall reduction in the range of 200:1 is achieved. For a
mufti-stage reduction gear, in particular a two-stage reduction
gear, the gear stage with the lower reduction may be designed as a
simple spur gear or as a belt gear, in particular as a toothed belt
gear. Use of a belt gear and/or toothed belt gear assists with the
decoupling of noise between the driving electric motor and the
other parts of the disc brake, and thus facilitates a comfortable
and quiet braking operation.
[0019] The electric motor and the reduction gear may be designed as
an independently operable subassembly which in particular is
standardized and combinable with various disc brakes of a design
type. This increases the production volume of such a motor/gear
unit, which is favorable for the unit cost. In addition, the
motor/gear unit designed as an independent assembly allows simple
mounting on the brake caliper of the disc brake in any given
angular position, so that spatial limitations at the installation
point of the disc brake may be taken into account by appropriately
positioning the subassembly differently.
[0020] According to one possible embodiment of the disc brake, it
is provided that the screw gear has or forms a spindle/nut
arrangement, and has a threaded spindle and a nut element that
meshes therewith. In one embodiment of the spindle/nut arrangement,
the threaded spindle is displaceably fixed with respect to the
brake caliper in the direction of the longitudinal axis of the
spindle/nut arrangement and is rotatable about the longitudinal
axis of the spindle/nut arrangement, and the nut element is
rotationally fixed with respect to the one actuating piston that is
used for carrying out the parking brake function and is
displaceable in the direction of the longitudinal axis of the one
actuating piston, so that the nut element is translationally moved
either into contact with the one actuating piston or away from the
one actuating piston due to a rotational motion of the threaded
spindle, depending on its rotational direction. The screw gear thus
has a technically simple implementation. For example, for this
purpose, the threaded spindle is displaceably fixed in the
direction of the longitudinal axis of the spindle/nut arrangement
and is supported or held on the brake caliper so as to be rotatable
about the longitudinal axis of the spindle/nut arrangement, and by
means of at least one connecting element, for example, the nut
element is held so that it is rotatably fixed with respect to the
one actuating piston, and displaceable in the direction of the
longitudinal axis of the one actuating piston.
[0021] The screw gear may also be implemented in a technically
simple manner when, according to another embodiment of the
spindle/nut arrangement, the nut element is displaceably fixed with
respect to the brake caliper in the direction of the longitudinal
axis of the spindle/nut arrangement and is rotatable about the
longitudinal axis of the spindle/nut arrangement, and the threaded
spindle is rotatably fixed with respect to the one actuating piston
and is displaceable in the direction of the longitudinal axis of
the one actuating piston, so that the threaded spindle is
translationally moved either into contact with the one actuating
piston or away from the one actuating piston due to a rotational
motion of the nut element, depending on its rotational direction.
For example, for this purpose, the nut element is displaceably
fixed in the direction of the longitudinal axis of the spindle/nut
arrangement and is supported or held on the brake caliper so as to
be rotatable about the longitudinal axis of the spindle/nut
arrangement, and by means of at least one connecting element, for
example, the threaded spindle is rotatably fixedly held with
respect to the one actuating piston and is displaceably held in the
direction of the longitudinal axis of the one actuating piston.
[0022] It is suitable for the thread of the spindle/nut arrangement
to be self-locking. As a result, the actuating piston, which is
actuated by the electric motor, is held in the particular position
in which it is brought by the spindle/nut arrangement. Due to the
self-locking mechanism, the position of the nut element on the
threaded spindle is maintained until the threaded spindle is
rotated by the electric motor. A separate lock for fixing the one
actuating piston in the setting position brought about by the
electric motor may be dispensed with.
[0023] According to one aspect of the invention, a disc brake
system for a vehicle is provided. The disc brake system includes
the above-described disc brake and a brake disc. In particular, the
brake disc is accommodated in the receptacle of the brake caliper
of the disc brake, so that the brake sides of the receiving space
face a respective flat side of the brake disc.
[0024] According to another aspect of the invention, a parking
brake system for a vehicle is provided. The parking brake system
has the above-described disc brake and/or the above-described disc
brake system, which utilizes the above-described electric motor for
carrying out a parking brake function or a hand brake function.
[0025] One possible embodiment of the parking brake system includes
an electronic control unit for controlling the electric motor, the
control unit and the electric motor being designed to set a braking
force, exerted by the at least one associated brake shoe, according
to one or more default values, in particular to set a braking force
in a continuously variable manner, to carry out parking braking.
For example, the default values may contain or be based on
information concerning the inclination of the roadway and/or the
friction coefficient of the road surface and/or the instantaneous
driving or standstill state of the motor vehicle and/or parameters
of the motor vehicle such as the load state. Controlled setting of
the braking force exerted by the at least one associated brake shoe
is thus made possible, and braking force metering, for example for
comfortable starting of the motor vehicle, in particular on an
inclined roadway, may be carried out.
BRIEF DESCRIPTION OF THE FIGURES
[0026] Further particulars and features of the invention result
from the following description of one exemplary embodiment with
reference to the drawings, which show the following:
[0027] FIG. 1 shows one possible embodiment of a disc brake in a
top view,
[0028] FIG. 2 shows a portion of the disc brake according to FIG. 1
as a view in the direction of the arrow X in FIG. 1,
[0029] FIG. 3 shows the disc brake according to FIG. 1 in a section
perpendicular to the plane of the drawing along the center axis A
of the disc brake, and
[0030] FIG. 4 shows a portion of the disc brake according to FIG. 1
as a view in the direction of the arrow Y in FIG. 1.
DETAILED DESCRIPTION
[0031] FIGS. 1 through 4 show schematic illustrations of a disc
brake 1. The disc brake 1 is a vehicle brake, for example, and may
be used in a motor vehicle, for example a passenger vehicle or a
truck. FIG. 1 shows the disc brake 1 in a top view, illustrating
individual components of the disc brake 1 in a partial sectional
view. FIGS. 2 and 4 each show a different view of a portion of the
disc brake 1. FIG. 3 shows the disc brake 1 in a sectional
illustration. In addition to the disc brake 1, a brake disc 100
schematically indicated by way of example is illustrated in FIG. 3.
The brake disc 100 and the disc brake 1 form, for example, a disc
brake system 200 or at least integral parts of the disc brake
system 200.
[0032] As is apparent in particular from FIG. 1, the disc brake 1
includes a brake carrier 10, a brake caliper 20, multiple brake
shoes 30, 30', 31, 31', and an actuating piston 40. A region of the
actuating piston 40 is shown in a partial sectional view in FIG. 1.
The brake carrier 10 is stationarily mountable with respect to a
vehicle (not illustrated in FIGS. 1 through 4). For this purpose,
the brake carrier 10 has at least one, for example two mounting
points 11, 11' for mounting on the vehicle. The mounting points 11,
11' may be formed by a through hole or a through borehole, or a
blind hole, or a blind borehole, in particular a threaded hole
(FIG. 2).
[0033] The brake caliper 20 is movably guided on the brake carrier
10 in the direction of the center axis A of the disc brake 1. The
brake caliper 20 forms a receiving space 21 for the brake disc 100,
the receiving space 21 having two brake sides 22, 23 with regard to
the brake disc 100, as is apparent in particular from FIGS. 1 and
3. At least one circular section or circular segment of the brake
disc 100 is preferably accommodated by the receiving space 21. For
example, for this purpose the brake caliper 20 may overlap the
brake disc 100. The brake caliper 20 may have a multi-part, for
example a two-part, design. For example, the brake caliper 20 has
at least two brake caliper sections 20.1, 20.2 that are mounted
opposite one another by means of at least one mounting element
20.3, in particular a screw bolt. The brake carrier 10 may also
have a multi-part, for example a two-part, design. For example, the
brake carrier 10 has a bridge section 10.1 that is fastened to the
brake carrier 10 by means of at least one connecting element 10.2
and overlaps the brake disc 100. A portion of the brake caliper 20
may be connected thereto.
[0034] With regard to one possible installation state of the disc
brake 1 on the vehicle, in the following discussion, the brake side
22 is also referred to as a vehicle inner side, and the brake side
23 is also referred to as a vehicle outer side. In this regard, the
brake disc 100 is used, for example, as a partition component for
differentiating between the vehicle inner side and the vehicle
outer side. Components of the disc brake 1 that are situated in the
direction according to arrow P1, starting from the brake side 22,
are thus to be associated with the vehicle inner portion, and
components that are situated in the direction according to arrow
P2, starting from the brake side 23, are to be associated with the
vehicle outer portion of the disc brake 1 (FIGS. 1 and 3).
[0035] The disc brake 1 may be utilized as a high-performance
brake. For this purpose, the brake caliper 20 is preferably
designed as a floating frame. In addition, on both the brake sides
22, 23 at least two of the brake shoes 30, 30', 31, 31' are
respectively spaced apart from one another (FIG. 4). In particular,
the brake shoes 30 and 30' are associated with the brake side 22,
and the brake shoes 31 and 31' are associated with the brake side
23, as is apparent in particular from FIG. 1. Due to a separate
arrangement between the brake shoes 30, 30' of the brake side 22
and between the brake shoes 31, 31' of the brake side 23, in each
case a space 36 or intermediate area is preferably formed that is
free of a friction lining 32, 32', 33, 33' and therefore exerts no
braking action during a braking operation.
[0036] Under the aspect of the high-performance brake, the disc
brake 1 preferably has at least one further actuating piston 40'
that is provided in addition to the actuating piston 40. The
actuating piston 40' is not explicitly visible in FIGS. 1 through
4. In FIG. 1, at least one housing section of the brake caliper 20
is indicated in which the actuating piston 40' is accommodated.
Reference numeral 40' is therefore assigned to this housing
section, although it is intended to denote the actuating
piston.
[0037] The actuating pistons 40, 40' are accommodated in the brake
caliper 20 so as to be displaceable in the direction of their
longitudinal axis 41 or 41', respectively, and thus displaceable,
for example, in the direction of the center axis A. The actuating
pistons 40, 40' are preferably situated on a vehicle inner portion
20.2 or section of the brake caliper 20. Two of the brake shoes 30,
30', 31, 31', in particular the brake shoes 30, 30' associated with
the brake side 22, are preferably respectively associated with one
of the actuating pistons 40, 40', for example in such a way that
upon actuation, the associated brake shoes 30, 30' are directly
pressed against the brake disc 100 by the actuating pistons 40,
40'. The brake shoes 30, 30' are preferably guided on the brake
carrier 10 via guides, so that the brake shoes 30, 30' may carry
out a pressing motion against the brake disc 100. By means of the
guides, the brake shoes 30, 30' are preferably supported on the
brake carrier 10 against braking forces.
[0038] The other of the brake shoes 30, 30', 31, 31', in particular
the brake shoes 31, 31'' associated with the brake side 23, are
preferably situated on a vehicle outer portion or section 20.1 of
the brake caliper 20. These brake shoes 31, 31' are preferably to
be actuated by displacing the brake caliper 20, i.e., indirectly.
For example, the brake shoes 31, 31' are held on a transverse yoke
37 of the brake caliper 20. The transverse yoke 37 may have
multiple pin elements 38 that are used for supporting and/or
guiding the associated brake shoes 31, 31'. The brake shoes 31, 31'
are supported on the brake carrier 10 against braking forces via
the connection of the brake caliper 20 to the brake carrier 10.
[0039] The brake shoes 30, 30', 31, 31' preferably have the
friction lining 32, 32', 33, 33', respectively, that is mounted on
a lining carrier 34, 34', 35, 35', respectively, or a back plate.
For example, for the brake shoes 30, 30' the respective lining
carrier 34, 34' is movably guided on the brake carrier 10 by means
of the guides. For example, for the brake shoes 31, 31' the
respective lining carrier 35, 35' is held on the brake caliper 20,
in particular the transverse yoke 37.
[0040] As is apparent in particular from FIGS. 2 and 3, the brake
caliper 20 is displaceably guided on the brake carrier 10 by at
least one, preferably two, guide elements 12, 13, in particular
guide bolts. For this purpose, the guide elements 12, 13 are
preferably situated between the brake shoes 30, 30' of the brake
side 22 and between the brake shoes 31, 31' of the other brake side
23. For example, the actuating pistons 40, 40' are situated on the
brake caliper 20 symmetrically with respect to an axial center
plane D of the brake carrier 10. The guide elements 12, 13 are
preferably situated in the axial center plane D, and in the radial
direction are spaced apart from one another with respect to the
center axis A of the disc brake 1 and extend, for example, parallel
to the center axis A (FIGS. 1 and 3). For example, the guide
elements 12, 13 are associated with the vehicle inner portion or
section 20.2 of the brake caliper 20. For guiding and/or supporting
the brake caliper 20 with respect to the brake carrier 10, a
further guide element 14, for example a bolt element, may be
provided that is associated with the vehicle outer portion or
section 20.1 of the brake caliper 20.
[0041] The disc brake 1 has a service brake function. The actuating
pistons 40, 40' are hydraulically actuated for this purpose. The
actuating pistons 40, 40' are preferably designed as hollow
pistons, and in each case have an interior space or cavity 42. In a
pressure space 26 via an inlet 25, by means of a hydraulic fluid, a
brake pressure is generated which moves the two actuating pistons
40, 40' in the direction according to the arrow Y. The brake shoes
30, 30' hereby come into contact with the brake disc 100 on its one
outer side. Due to the "action=reaction" principle, the movement of
the actuating pistons 40, 40' correspondingly moves the entire
brake caliper 20 in the opposite direction, i.e., in the direction
according to the arrow X (FIG. 1). The brake caliper 20, which
overlaps the brake disc 100, thus brings the brake shoes 31 and 31'
into contact with the brake disc 100 on its other outer side.
[0042] The interior space 42 of each actuating piston 40 or 40',
utilized as a hydraulic chamber, is preferably sealed off with
respect to the brake caliper 20 by means of a sealing element 43.
The sealing element 43 may be a sealing ring that is mounted on the
outer circumference of the associated actuating piston 40 or 40'
and is supported against the wall of the inner circumference of the
associated piston receptacle of the brake caliper 20.
[0043] The disc brake 1, in addition to the service brake function,
also has a parking brake function or hand brake function that can
also be used as an emergency brake function. For carrying out the
parking brake function, one of the actuating pistons 40, 40', in
particular the actuating piston 40, is actuatable by means of an
electric motor 50. The electric motor 50 may in principle also be
used so that the one actuating piston 40 is actuated by the fact
that both types of actuation overlap; i.e., a hydraulic actuating
force and a mechanical actuating force are simultaneously exerted
on the actuating piston 40. The electric motor 50 is schematically
illustrated in FIG. 1 by way of example.
[0044] The electric motor 50 is preferably situated between the
actuating pistons 40 and 40', and a longitudinal axis 52 of the
electric motor 50 and an output shaft 51 of the electric motor 50,
and the longitudinal axis 41 of the actuating piston 40 are axially
offset, for example situated axially parallel to one another. For
example, the electric motor 50 engages with an open space 24 of the
brake caliper 20 that is present, for example, between the
actuating pistons 40 and 40'. The longitudinal axis 52 of the
electric motor 50 and/or the output shaft 51 of the electric motor
50 preferably coincide(s) with the center axis A of the disc brake
1.
[0045] The electric motor 50 may be operatively connectable to the
actuating piston 40 via a screw gear 53 in order to carry out the
parking brake function. The screw gear 53 is preferably situated in
the interior space 42 of the one actuating piston 40. For this
purpose, the one actuating piston 40 is preferably open on one
side, and with a dosed side faces the associated brake side 22. The
other actuating piston 40' may have a similar design and
arrangement. In addition, the other actuating piston 40' with an
open side may face the associated brake side 22.
[0046] The screw gear 53 may be designed as a spindle/nut
arrangement. The spindle/nut arrangement has a threaded spindle 54
and a nut element 55 that meshes therewith. The threaded spindle 54
is displaceably fixed on the brake caliper 20, for example by means
of a bearing 59, in the direction of a longitudinal axis 58 of the
spindle/nut arrangement, and is supported so as to be rotatable
about the longitudinal axis 58 of the spindle/nut arrangement. The
nut element 55 is held so that by means of at least one securing
element 57 and is rotatably fixed with respect to the actuating
piston 40, and displaceable in the direction of the longitudinal
axis 41 of the actuating piston 40. A rotational motion of the
threaded spindle 54 as a function of its rotational direction is
thus possible, via which the nut element 55 is translationally
moved either into contact with the actuating piston 40 or away from
the actuating piston 40. The threaded spindle 54 is preferably
sealed off with respect to the brake caliper 20 by a sealing
element 59.1, in particular a shaft seal, in order to ensure
seal-tightness of the pressure space 26.
[0047] The nut element 55 with its outer circumferential surface is
preferably at least partially guided on the inner circumference of
the actuating piston 40. For example, an end area 56 of the nut
element 55, in particular the end area 56 facing the associated
brake shoe 30, is radially expanded and used as a guide surface
with respect to the inner face of the actuating piston 40. The
securing element 57 is preferably a bolt element or a pin element
38 which at one end is fastened to a wall section of the actuating
piston 40, preferably provided within the interior space 42 of the
actuating piston 40 and, for example, with its longitudinal axis 41
situated axially parallel to the longitudinal axis 58 of the
actuating piston 40.
[0048] The electric motor 50 and the screw gear 53 are preferably
in drive connection with one another via a reduction gear 60. For
example, the reduction gear 53 [sic; 60] has a multi-stage, in
particular a two-stage, design. The reduction gear 53 [sic; 60] may
be a spur gear and/or belt gear. For example, the reduction gear 60
allows an overall reduction of the output shaft 51 of the electric
motor 50 to the screw gear 53, in particular the threaded spindle
54, of approximately 200:1. The reduction gear 60 is preferably
situated in the area of the vehicle-side end of the disc brake 1.
For example, the reduction gear 60 connects the preferably axially
parallel shafts, namely, the output shaft 51 of the electric motor
50 and the input shaft of the screw gear 53, in particular the
threaded spindle 54, to one another.
[0049] In the present description, reference to a certain aspect or
a certain embodiment or a certain configuration means that a
certain feature or a certain property, described in conjunction
with the particular aspect or the particular embodiment or the
particular configuration, is at least contained therein, but does
not necessarily have to be contained in all aspects or embodiments
or configurations of the invention. It is expressly noted that any
combination of the various features and/or structures and/or
properties that are described with regard to the invention is
encompassed by the invention, provided that the context does not
explicitly or unambiguously indicate otherwise.
[0050] The use of single, or all, examples, or wording in the text
by way of example is intended solely to elucidate the invention,
and does not represent a limitation with regard to the scope of the
invention, unless stated otherwise. In addition, no expression or
wording of the description is to be construed in such a way that it
involves an element that is not claimed, but is essential for the
practice of the invention.
* * * * *